Air conditioning system



Oct. 15, 1940. J, HAlNEs 2,218,468

AIR CONDITIONING SYSTEM Filed Feb. 25. 1957 zsnets-sheet 1 REHEATER CONDENSER gwue/wtoc PREHATER EXHAUST @7070: l iijiaz'rzes Oct. 15, 1940. J 5 HAINES 2,218,468

AIR QONDITIONING SYSTEM Filed Feb. 25, 1957 2 Sheets-Sheet 4 5548 Gnm w Patented Oct. 15, 1940 UNITED STATES PATENT OFFICE 2,218,468 AIR CONDITIONING SYSTEM Application February 23, 1937, Serial No. 127,128

14 Claims.

This invention relates generally to the art of air conditioning and is more particularly concerned with automatic control arrangements for air condition systems.

The primary object of my invention is to provide a relatively simple and dependable control arrangement for automatically controlling an air conditioning system to maintain desired indoor conditions throughout the entire year, such system effecting control of cooling, control of heating, control of ventilation, control of humidification, and control of dehumidification, these various conditioning functions being utilized in varying degrees and sequence to economically maintain the desired indoor conditions regardless of conditions exterior to the conditioned space.

In accordance with a preferred form of my invention, a conditioning chamber is provided 2 through which a mixture of return air and fresh air is passed to be conditioned, the thereby conditioned air being discharged from such chamber to the spaces to be conditioned. Located within the conditioning chamber is a preheating coil 25 and a spray device around which is placed a bypass for the return air. The preheater and spray device are controlled by a pair of dew-point con trollers which act to maintain the dew-point temperature of the air issuing from the spray with- 30 in a predetermined range. During the cooling cycle the proportions of the air passed through and by-passed around the spray device are varied by a by-pass damper which damper is controlled by a temperature controller responsive to 55 the temperature of the air within the conditioned space. This controller is in turn compensated for changes in humidity by a humidostat located within the conditioned space to maintain a desired comfort or eifective temperature. In addition, the temperature controller is adjusted by an outside temperature responsive controller for varying the inside temperature maintained in accordance with outside temperature. For effecting heating, a reheater is placed in the conditioning chamber downstream of the spray device and the by-pass, and this reheater is controlled by a spaced temperature responsive controller which acts to cause steam to be supplied to the reheating coil when the temperature with- I in the space falls to a predetermined value. At this time the control of the by-pass damper is taken away from the controllers mentioned and the by-pass damper is closed completely to cause all of the air to be passed through the spray device. Also during the heating cycle the temperature of the air in the various zones is controlled by booster heaters for each zone, these booster heaters being controlled by temperature responsive controllers in the respective zones.

One object of my invention is to provide an air conditioning system of the type wherein the air to be conditioned is passed through a spray, with automatic control means for maintaining the temperature of the air issuing from the spray Within a predetermined range, such control means acting automatically to operate either heating or cooling devices in the appropriate manner to maintain the desired condition.

Another object of my invention is the provision of a by-pass around an air conditioning device such as a spray with an automatic control device for varying the air passed through and around the spray in accordance with the refrigeration load, such control device acting also to prevent the flow of air through the by-pass when a heater is placed in operation.

A further object is the provision of an air conditioning system in which a spray device is provided with controlling means for maintaining the dew-point of the air within a predetermined range and in which a by-pass is placed around such spray device, the proportions of the air passed through and around the spray device being controlled during the cooling cycle in accordance with the demand for cooling, and in which the by-pass is automatically closed when the heating cycle begins.

A still further object is to provide a yeararound air conditioning system in which a low limit controller is located in the discharge duct for preventing the temperature of the air delivered to the conditioned space from falling below a predetermined value during the heating cycle, such low limit controller being automatically placed out of operation during the cooling cycle.

Another object of my invention is" to provide a zoned heating system in which the control of a main heating coil for supplying heated air to a plurality of zones is controlled in accordance with the average requirements for heat of all of the zones, and in which the temperature'of each individual zone is controlled by means of a temperature controller which controls the supply of heat to a booster heater for that zone.

Another object is the provision of a refrigeration system for supplying a chilled cooling medium to a heat exchanger, in which the now of cooling medium is controlled in accordance with the cooling requirements and in which the operation of a refrigeration system is stopped whenever the flow of cooling medium is reduced to a predetermined value.

Further objects and advantages of my invention will appear from the following detailed description and from the appended claims.

For a full disclosure of my invention, reference is made to the following detailed description and to the drawings, in which Figure 1 shows diagrammatically a summerwinter air conditioning system which forms my invention; and

Figure 2 shows a wiring diagram of part of the control system illustrated in Figure 1.

Referring to Figure 1, reference character I indicates an air conditioning chamber. Located within conditioning chamber .I is a preheater coil 2, a spray pipe 3 and a reheater 4. The discharge end of the conditioning chamber I is connected to a fan 5 which discharges into a delivery duct 6, this duct having branches 1 and 8 leading to the conditioned spaces 9 and III. A return air duct I I is connected to the spaces 9 and II] in a suitable manner (not shown). Duct II is connected to a by-pass duct I2 which joins the conditioning chamber I at a point intermediate the spray 3 and the reheater 4. Duct I I is also connected to an auxiliary return duct I la which leads to a duct I4 which in turn is connected to the inlet end of the conditioning chamber I adjacent to the fresh air inlet duct I5, the duct I4 also leading to a suitable discharge (not shown). A suitable damper I6 may be provided in the fresh air duct I5 for controlling the quantity of fresh air admitted to the conditioning chamber I. Also, dampers I! and I8 may be provided for controlling the proportions of return air discharged into the conditioning chamber I and discharged from the building through the discharge duct I4. By this arrangement a mixture of fresh and return air is passed through the conditioning chamber and is then delivered to the spaces to be conditioned. Also the return air is in part exhausted from the building, passed across the preheater tothe spray 3, and bypassed therearound.

A receiver 20 is provided for supplying chilled water to the spray pipe 3. This receiver is connected at its lower end by a pipe 2I to the cold water inlet of the three-way valve 22. The intermediate chamber of the three-way valve 22 is connected by a pipe 23 to the inlet of a pump '24, the discharge side of such pump being connected by a pipe 25 to the spray pipe 3. Located below the spray pipe 3 is a trough 26 for collecting the water issuing from said spray pipe. The trough 26 is connected to a drain pipe 21 having a branch 28 leading back to the receiver 20 and a branch 29 which leads to the return water inlet of the three-way valve 22. Located within the casing of the three-way valve 22 is a valve member 30, the valve stem thereof being secured to a gear rack 3|, which gear rack cooperates with a pinion 32 which is secured to the shaft of a proportioning motor 33. This proportioning motor may be of the type shown and described in Patent No. 1,989,972 issued to Lewis L. Cunningham on May 5, 1935.

The proportioning motor 33 is adapted to be controlled by a temperature controller generally indicated at 35. The controller 35 comprises a bellows 36 which is secured at its lower end to a suitable support 31 and which at its upper end is provided with an abutment 38 which cooperates with the actuating arm 39 of a bell crank lever 40. Bell crank lever 40 also includes a control arm M which engages a control resistance 42. The control arm 4| and the control resistance 42 are connected to the proportioning motor as indicated in the Cunningham patent above referred to. Also connected to the actuating arm 39 of bell crank lever 40 is a spring 43 which is secured to the fixed support 31. The interior of the bellows 36 is connected to a capillary tube 44 which leads to a temperature control bulb 45 located in the conditioning chamber I at a point between the spray pipe 3 and the point at which by-pass duct I2 joins.the conditioning chamber. The bulb 45, tube 44 and bellows 36 contain a volatile fluid as well known in the art. Therefore, as the temperature of the air issuing from the spray 3 increases, the pressure of the volatile fill will increase, this causing expansion of the bellows 36 and consequent movement 'of the control arm 4I across the control resistance 42 in a counter-cockwise direction. Conversely, upon a fall in temperature at the' bulb 45 the bellows 36 will contract thereby permitting the control arm M to be moved in the opposite direction under the action of the spring 43.

The proportioning motor 33 is arranged to assume angular positions corresponding to the positioning of the control arm M on the control resistance 42. The controller 35 may be so designed and adjusted that when the temperature at the bulb 45 is 50 F. the control arm M will engage the extreme right-hand portion of control resistance 42, while when the temperature at bulb 45 is increased to 56 F. the control arm M will engage the extreme left-hand end of control resistance 42. tioning motor 33 relative to the controller 35 may be such that the valve member is moved to its extreme upper position when the control arm 4I engages the extreme left-hand end of control resistance 42. Therefore, when the temperature of the air issuing from the spray pipe 3 is up to 56 F. the three-way valve will be positioned to cause flow of cold water from the receiver directly to the spray pipe 3 without admixture of return water. The proportioning motor 33 is also arranged with respect to the valve member 30 so that it will move said valve member to its extreme lower position when the control arm 4I engages .the extreme right-hand end of control resistance 42. By this arrangement, when the temperature of the air issuing from the spray falls to 50 F. no delivery of chilled water from the receiver through pipe 2I will take place, but a circulation of return water through pipe 21 and branch 29 to the delivery pipe 23 will occur. For values of temperature intermediate 50 F. and 56 F. the proportioning motor will position valve member 30 at intermediate positions in accordance with the temperature at bulb 45, this causing a mixture of chilled water through pipe 2| and return water through pipes 21 and 29 to be supplied to the spray pipe 3, the proportions of the mixture being varied to cause the temperature of the spray water to be decreased as the temperature at the bulb 45 increases.

In order to chill the water in the receiver 20 a refrigeration coil 50 is located therein, this coil forming part of a compression refrigeration system including a compressor 5|, a condenser 52- and an expansion valve 52a. As such refrigeration systems are well known in the art a further description of such system appears to be unnecessary. The compressor motor is con- The arrangement of the proporv trolled by a magnetic starter or relay generally indicated at 53, this relay comprising switch arms 54 and 55 cooperating with respective contacts 56 and. 51.. Switch arms 54 and 55 are connected in a suitable manner to a plunger located within the coil 58. When this coil is energized the switch arms 54 and 55 are moved into engagement with the contacts 56 and 51, this causing the compressor motor to be connected to the line wires 59 and 60, thereby placing the compression refrigeration system in operation to cool the water within receiver 20.

When relay coil 58 is deenergized, however, the

switch arms 54 and 55 are moved away from their respective contacts under the action of gravity or springs, not shown, thereby placing the refrigeration system out of operation.

One end of the relay coil 58 is connected by a wire M with the low voltage secondary 02 of transformer Me, the primary of which is connected to line wires 59 and 80. The other end of relay coil 58 is connected by wire 83 to the mercury switch 64 of the temperature controller generally indicated as 65. The temperature controller 85 comprises a bellows 66 cooperating with the pivoted switch carrier 61 which carries the mercury switch 64. The bellows 66 is connected by a capillary tube 68 to a control bulb 60 located within the receiver 20. The arrangement is such that when the temperature within receiver rises above a predetermined value, for instance 40 F., the bellows 66 will be expanded sufiiciently to tilt the mercury switch 64 to closed position. When, however, the temperature of the water within the receiver is below the predetermined value the bellows 86 will contract sufliciently to cause the mercury switch 64 to be tilted to open position. The mercury switch 84 is connected by a wire 10 to an auxiliary switch ll which is mounted upon the shaft of the proportioning motor 33, the other terminal of the auxiliary switch H being connected to the secondary 82 of the transformer 62a by a wire 12. The auxiliary switch H is arranged to close whenever the valve member of the three-way valve 22 is moved from its extreme lower position but to open when the valve member 30 reaches its extreme lower position. Assuming auxiliary switch H to be closed due to the three-way valve being moved from its extreme lower position, if the temperature in the receiver should rise above 40 F., the relay coil 58 will be energized as follows: transformer secondary 62, wire 6!, relay coil 58, wire 83, mercuryswitch 64, wire l0, auxiliary switch ll, and wire 12 to transformer secondary 62. This will cause operation of the refrigeration system to lower the temperature of the water within receiver 20. When this temperature is lowered sufficiently the mercury switch M will be tilted to open position, this causing deenergization of relay coil 58 and consequent stopping of the compressor 5i parent that by this arrangement the controller 85 will act to maintain the temperature of the water within the receiver 20 below a predetermined value, such as 40 F., whenever the threeway valve 22 is adjusted so asito deliver water from the receiver 20 to the spray pipe 3. When, however, the three-way valve is adjusted so as to prevent-delivery. of water from the receiver, the refrigerating system will be placed out of operation by the auxiliary switch H regardless of the temperature of the water within receiver 20.

For controlling the flow of heating medium into the preheater coil 2 a valve 15 is provided,

It should therefore be apthis valve having a gear rack 16 secured to its valve stem. Cooperating with the gear rack l6 isa pinion H which is secured to the shaft of a .proportioning motor it. This proportioning motor is preferably of the type illustrated in the Cunningham patent hereinbefore mentioned, and

to the controller and comprises a bellows'tl' to which is secured a capillary tube 82 which is con-- nected to a control bulb 83 located adjacent the control bulb 35. The temperature controller tt also comprises a control arm M cooperating with a control resistance 85, this control arm and con-1 trol resistance being connected to the proportioning motor l8. The controller 80 is preferably designed and adjusted so that when the temperature at control bulb 83 is at or above 44 F. the control arm Mwill engage the extreme left-hand end of the control resistance 85. The controller 80 is also arranged so that when the temperature at control bulb 83 fallsto F. the control arm M will traverse the entire control resistance 85 and engage the extreme right-hand end thereof. The proportioning motor i0 is so associated. with the control arm 84 and the control resistance 85 that it assumes angular positions corresponding to the position of control arm 80 on the control resistance 85. The arrangement is such that when the control arm 8t engages the extreme left-hand end of control resistance 85 the proportioning motor 78 will move the valve to a full closed position as illustrated. However, as the control arm 84 moves across control resistance 85' from left to right the proportioning motor 18 will progressively open the valve, and when the arm 84 engages the extreme right-hand end of resistance 85 the valve will be moved to a full open position. It should therefore be apparent that when the temperature of the air issuing from the spray is above 44. F. the valve 715 will be fully closed thereby preventing any heating of the air by preheater 2. As the temperature of the sprayed air falls below 44 F., however, the valve 'l5 will be progressively opened and will reach full open position when the temperature ofthe sprayed air falls to 40 F.

From the foregoing, it should be seen that the controllers 35 and 80 act to maintain thetemperature of the sprayed air within a predetermined range, that is, between 40 F. and 56 F. When the temperature of the sprayed air is at 56 F. the three-way valve 22 will be so positioned that only cold water from the receiver 20 is delivered to the spray pipe 3. As the temperature of the sprayed air falls, however, the three-way valve will be moved to progressively decrease the proportion of cold water from receiver 20 and'increase the proportion of recirculated water from trough 26 which is passed through the spray pipe 3. When the sprayed air temperature falls to F. the threeeway valve 22 will be positioned to pass all recirculated water to the spray pipe 3 and to prevent delivery of water from the receiver 20 to said spray pipe. At the same time the auxiliary switch M will act to place the refrigeration system out of operation. As the sprayed air temperature continues to fall entirely recirculated water will be sprayed over the air. When the temperature falls to 44 F., however, the steam valve 15 will begin to open and upon further fall intemperature the steam valve will be opened still more, reaching full open position when the sprayed air temperature falls to 40 F. Therefore, as the sprayed air temperature falls from a maximum to a minimum the temperature of the sprayed water is gradually reduced and upon further reduction in temperature of the air the preheater coil is placed into operation.

Located in the by-pass duct I2 is a by-pass damper I3, this damper being controlled by a proportioning motor 90. The proportioning motor 90 is controlled primarily by a return duct temperature controller 9I Proportioning motor 90 is also controlled by a humidity controller 92 located within one of the conditioned spaces. In addition the proportioning motor 90 is controlled by an outside temperature responsive controller 93. The construction and operation of these controllers will be described in detail in connection with Figure 2. In general the purpose of these con- I the temperature controller 9| in accordance with.

outdoor temperature in accordance with customary practice. The specific manner in which these various controllers cooperate in the control of the by-pass damper I3 will be described in detail later in this specification.

A valve 95 is provided for controlling the flow of heating medium to the reheater coil 4. Attached to the stem 96 of valve 95 is a gear rack 91 which is arranged to engage a pinion 98 secured to the shaft of the proportioning motor 99. This proportioning motor 99 will be described in detail in connection with Figure 2 and is controlled by means of a return duct temperature controller I00 and also by a low limit controller IOI which is responsive to the temperature of the air in the delivery duct 6. In order to place the low limit controller Illl out of operation during the cooling cycle of the system the controller I02 is provided, which is responsive to the temperature of the air in the return duct II.

The controller I00 comprises a bellows I04 which is secured at its lower end to a suitable fixed support and which at its upper end cooperates with a bell crank lever I05 consisting of an actuating arm I06 and a control arm I01,

' said control arm I01 being arranged to engage a control resistance I08. The interior of the bellows I04 is connected by a capillary tube I09 to a control bulb IIO located in the return air duct II. The control bulb IIO, tube I09 and bellows I04 contain a suitable volatile fluid, as iswell known in the art. Upon an increase in temperature at control bulb IIO the pressure of the volatile fill will increase, this causing the bellows I04 to expand, this action resulting in movement of the control arm I01 across resistance I08 in a counterclockwise direction. Upon a decrease in temperature at bulb III! the pressure of the volatile fill will decrease, this permitting the control arm I0! to be rotated in the opposite direction under the action of a spring III. The controller I09 is preferably designed and adjusted so that the control arm I01 will engage the extreme left end of resistance I08 when the temperature of the return air is 71 F; and to engage the extreme right end of resistance I08 when the return air temperature falls to 69 F.

The low limit controller IOI may be formed similarly to the controller I00. This instrument,

' however, includes a bulb II5.located in the delivery duct 6, this bulb beir: connected to the bellows II6 by a capillary tube II'I. This instrument ispreferably designed and adjusted so that when the return air temperature is above 63 F. the control arm II8 will engage the extreme lefthand end of control resistance II9. When the return air temperature falls to 60 F'., however, the control arm I I8 will engage the extreme righthand end of control resistance H9.

The controller I02 includes a bellows I which is connected by a capillary tube I2I to a control bulb I22 located in return air duct II. The bellows I20 is arranged to cooperate with a mercury switch carrier I23 which carries a double ended mercury switch I24. This controller is arranged so that when the return air temperature is above -'71 F. the mercury switch I24 will be tilted to the position shown. When, however, the temperature within the return air duct falls below this value the mercury switch I24 will be troller I0l out of operation whenever the return air temperature is above 71 R, which is an indication that the system is operating on the summer cycle.

Located within .the branch delivery ducts I and 8 are booster heating coils I and I3I respectively. These booster heating coils are provided with heating fluid controlling valves I32 and I33, these v alves having gear racks I34 and I35 secured to their respective valve stems. The gear rack I34 of valve I32 is arranged to cooperate with a pinion I36 secured to .the shaft of a proportioning motor I31 while a similar proportioning motor I38 is arranged to drive a pinion I39 cooperating with a gear rack I35 of the valve I33. The proportioning motors I31 and I38 are controlled by temperature controllers I40 and I M respectively, these temperature controllers being located within the spaces 9 and I0. Temperature controllers I40 and MI are of usual form and each consists of a bellows I42 which is filled with a volatile fluid and which is arranged to actuate a bell crank lever I43 having a control arm I44 engaging a control resistance I45. These instruments may be so designed and adjusted that the control arms I44 will engage the extreme left-hand end of control resistances I45 when the space temperature is 71 F. and so that the control arms I 44 will engage the opposite ends of control resistances I 45 when the space temperature is 69 F. Furthermore, each of these controllers is associated with its respective proportioning motor in a manner to cause the corresponding valve to be closed entirely when the space temperature is 71 F. and to gradually open the steam valve as the space temperature falls, the valve assuming a wide open position when the space temperature falls to 69 F. By this arrangement the proper temperature will be maintained within the spaces 9 and I0 by the action of the booster heaters I30 and I3I in cooperation with the heating effect of the reheater 4. As hereinbefore mentioned, the reheater 4 is controlled by the controller I00 which is responsive to the temperature of the air in the return air duct II. As the air within the return duct II is a mixture of the air taken from all of the spaces its temperature will be an average of the temperatures of the various spaces and hence the reheater 4 will be controlled in accordance with the average requirement for heat of the total number of spaces. The booster heaters I30 and I3I, however, will be individually controlled in a manner to maintain the temperature in their respective zones constant. Thus should the heating load of the spaces 8 and I0 vary, the controllers I40 and I will changethe positions of the booster heater valves, thereby changing the amount of additional heat supplied in a manner to maintain constant temperature conditions.

Referring now to Figure 2, the construction and operation of the by-pass damper controlling proportioning motor 90 and its controllers will be described in detail. The by-pass damper I3 is herein illustrated as comprising a plurality of rotatable louvres, these louvres being connected together by an actuating member I which in turn is secured to the shaft I52 of the proportioning motor 90. The proportioning motor 90 comprises a first rotor I53 and a second rotor I54, these rotors being secured to a shaft I55 carrying a pinion I56 of the gear train I51. The last gear of the gear train is secured to the shaft I52 and in this manner the rotors I53 and I54 drive the shaft I52. Cooperating with the rotor I53 is a field coil I58 and cooperating with the rotor I54 is a similar coil I59. The rotor I53 and its associated coil I.58 form one motor, this motor when energized acting to drive the shaft I52 in one direction. The rotor I54 and its associated coil I59 form a second motor, this motor being arranged when energized to drive the shaft I52 in the opposite direction to that caused by operation of the other motor. The two motors, therefore, may be considered as a reversible electric motor. Also secured to the shaft I52 is a balancing arm I60 which is arranged to cooperate with a balancing resistance I6I. The arm I60 and resistance I6I therefore comprise a balancing potentiometer, this potentiometer being arranged so that thearm I60 contacts the extreme upper end of resistance I6I when the bypass damper I3 is moved to closed position. As the by-pass dampers are moved towards open position the balancing arm I60 is rotated by the ing with the control resistance I1I and'a corspaces is a humidity controller 92, this controller comprising a bell crank lever I having an actuating arm I8I and a control arm I82 which cooperates with a control resistance I83. Attached to the actuating arm I8I is a humidity responsive device, this device comprising a plurality of strands of humidity responsive material I84 secured at their upper and lower ends to clamping members I85 and I86 respectively. The upper clamping member I85 is secured to the actuating arm I8I while the lower clamping member is secured to a suitable fixed element I81. Also connected to the actuating arm I8I is a spring I88, this spring being in turn connected to a fixed support I89. Upon a decrease in humidity within the space, the strands I84 will decrease in length, this causing a 'downward movement of arm I 8| against the action of the spring I88 this resulting in movement of the control arm I82 in a counter-clockwise direction across the control resistance I83. Upon an increase in humidity the strands I84 will increase in length, this permitting the control arm I8I to be moved across the control resistance I83 in a clockwise direction under the action of the spring I88. This instrument may be designed and adjusted so that the arm I82 engages the extreme left-hand end of'resistance I83 when the relative humidity in the space is 40% and so that the arm I82 engages the extreme righthand portion of resistance I83 when the relative humidity is 60%.

Also controlling the proportioning motor 90 is the outdoor temperature responsive controller 93. This controller comprises a bellows I cooperating with a bell crank lever I95a having an actuating arm I91 and a control arm I98 engaging a control resistance I99. The bellows signed and adjusted so that when the return air duct temperature is above 80 F. the bellows I65 will be expanded sufficiently to cause the control arm I10 to engage the extreme left-hand end of the control resistance I1I. As the return air temperature falls below 80 F., however, the

bellows I65 will contract permitting the control I95 is connected by a capillary tube I96 to a control bulb I91 in the fresh air duct I5 (Figure 1). As the outdoor temperature increases the bellows I65 will expand, this causing rotation of the control arm I98 against the action of spring 200 across the control resistance I99 in a clockwise direction. Upon falling outdoor temperature the bellows I85 will contract and the control arm I98 will 'be moved in the opposite direction under-the action of the spring 200. This instrument may be adjusted so that the control arm I98 engages the extreme left-hand portion of resistance I99 when the outdoor temperature is 76 F. When the outdoor temperature rises to 100 F., however, the control arm I98 will engage the extreme right-hand end of theresistance I99.

Reference character 205 designates generally a balanced relay-comprising a U-shaped armature 206 which is pivoted at 201, and is provided with legs 208 and 209. Secured to armature 206 by means of an insulating member 2 I 0 is a switch I arm 2I I which is adapted to cooperate with contacts 2I2 and 2I3. Cooperating with the leg 208 of armature 206 is a relay coil 2 I4, a similar coil 2 I 5 cooperating with the leg 209. When the relay coils 2 I4 and 2I5 are equally energized the upward pulling eifect exerted upon the two legs of the armature 206 will be equalized and the armature will assume the position shown in which the switch arm 2 is disengaged from both contacts 2I2 and 2I3. If the relay coil 2I4 is energized to a greater extent than coil 2I5 the upward pulling efiect exerted upon the leg 208 will be greater than that exerted upon leg 209, this causing the armature 206 to be rotated in a clockwise direction bringing the switch arm 2 into engagement with contact 2I2. If, on the ment with contact arm 214.

other hand, the relay coil 2I5 is energized more highly than the relay coil 2I4, the armature will be rotated in the opposite direction bringing the switch arm 2 into engagement with the contact 2 I3.

Reference character 220' designates a step-down transformer having a high voltage primary 22I ccunected across the line wires 222 and 223. The low voltage secondary 224 of transformer 220 is connected by means of wires 225 and 226 to the lower end of the relay coil 2I4. The upper end of relay coil 2I4 is connected to the upper end of relay coil 2I5 by a wire 221 and the lower end of the relay coil 2 I 5 is connected by wires 228 and 229 to the transformer secondary 224. In this manner the relay coils 2I4 and 2I5 are connected in series across the transformer secondary 224. Connected to the wire 226 is a wire 23I which is in turn connected to a wire 232 leading to the right-hand end of control resistance I1I of temperature controller 9|. Also connected to wire 23I is a wire 233, this wire being connected to a wire 234 leading to one end of the balancing resistance I6I. The wire 233 is also connected to a wire 235 which leads to the left-hand end of the humidostat control resistance I83. Also connected to the wire 23I is a wire 236 leading to the right-hand end of the outdoor controller resistance I99. Connected to the lower end of the relay coil 2i 5 is a wire 231; this wire being connected to the left-hand ends of the resistance HI and resistance I99 by wires 238 and 239. A wire 240 leads from the junction of wires 238 and 239, this wire being connected to the lower end of balancing resistance I68 by a wire MI and being connected to the right-hand end of the humidostat control resistance I83 by wire 242. From the foregoing it should be apparent that the resistances I6I, I1I, I83 and I99 are connected in parallel with the serially connected relay coils 2I4 and 2I5 across the transformer secondary 224.

Mounted upon the main operating shaft 219 of the proportioning motor 99 for the steam valve 95 is a cam 21I. This cam is arranged to operate a switching device or auxiliary switch 212 which comprises a switch arm 213 formed as a cam follower, this switch arm being arranged to selectively engage the contact arm 214 or the contact arm 214a. The cam 21I is mounted upon the motor shaft 219 in such manner that when the valve 95 is completely closed, the recessed portion of said cam will engage the switch arm 213. this permitting said arm to engage the contact arm 214a. When, howeventhe steam Valve 95 is moved from closed position, the raised portion of the cam 21I will engage switch arm 213, this forcing said switch arm away from engage- Inent with contact arm 214a and into engage- The switch arm 2153 is connected to the Wire 221 which joins the upper ends of relay coils 2I4 and 2I5 means of wire 221a. To the contact arm 214a is connected a wire 219, this wire being connected to Wire 250 in; to rheostat 25L which in turn is con- Y vc1 d by wire 29! to the control arm I98 of the co troller t n QEl'Eltlli6 responsive ted to the junction of Wii this wire being col corrector resists 'c controller 9 e. no: on al \vi at so: and wire 25 3 arm I82 of the humidity respon- Connected also to the wire conncctL-p to the cunt 51 re controller 221 is a, wire 245, this wire leading to rheostat 246, this rheostat being in turn connected to the balancing arm I68 of the balancing potentiometer by wire 241. From the foregoing, it should be seen that the balancing arm I is always connected to the upper ends of relay coils 2 I 4 and 2 I 5, and that the control arms I10, I82 and I98 are connected to the upper ends of said relay coils so long as the steam valve 95 remains closed. This connecting of the balancing arm and the control arms to the connected ends of the relay coils 2I4 and 2I5 has the effect of placing part of the balancing resistance and of each control resistance in parallel with one of the relay coils, and the remaining parts of said resistances in parallel with the other of the relay coils.

Assuming the steam valve 95 to be closed with the balancing arm. I68 and the control arms I19, I82 and I98 in their mid-positions as shown, they will engage points on their respective resistances having the same potential as the junction of the relay coils 2I4 and 2I5. Under this condition no current will flow to or from the junction of relay coils 2I4 and 2I5 and hence the said relay coils will be equally energized, this causing the switch arm 2I I to be disengaged from both contacts 2I2 and 2I3. If now the return air temperature should fall, the control arm I10 of controller 9| will move along the control resistance I H to the right. This will have the effect of reducing the portion of resistance I1 I which is in parallel with the relay coil 2 I4 and of increasing the portion of resistance H! which is in parallel with the relay coil 2I5. This will cause the current flow in relay coil 2I4 to decrease and the current flow in relay coil 2I5 to increase. The relay coil 2 I 5 will thus become more highly energized than relay coil 2 I4 this having the action of rotating the armature 206 to bring the switch arm 2 into engagement with the contact 2I3. Engagement of the switch arm 2I I with contact 2I3 will establish an energizing circuit for the motor field coil I58 as follows: transformer secondary 224, wire 225, wire 260, field coil I58, wire 26I, contact 2I3, switch arm 2, wire 262, wire 228 and wire 229 back to transformer secondary 224. This will cause rotation of the proportioning motor shaft I52 in a direction to open the damper I3. At the same time the balancing arm I69 will be rotated downwardly across balancing resistance I6I, this having the effect of reducing the portion of balancing resistance I6I which is in parallel with relay coil 2I5 and of increasing the portion of resistance I6I which is in parallel with relay coil 2I4. The effect of this will be to decrease the current fiow in relay coil 2I5 and to increase the current flow in relay coil 2 I4, this action thereby compensating for the previous unbalancing effect initiated by the controller 9|. When the rotation of the proportioning motor shaft is sufficient to cause the balancing arm to be moved sufficiently to overcome the unbalancing efiect of controller 9I on the relay 285 the relay coils 2I4 and 2I5 will be again equally energized amt the switch arm 2II will be disengaged from the control arm 19 across the control resistance I 1 I. In other words, the more the temperature in return duct Ii decreases the further the move- Inert of l e dampers t-:.-i.vards closed position by Sill the proportioning motor 90 is necessary before the relay 205 will become rebalanced.

If the temperature within the return duct should increase the control arm I10 will be moved across the control resistance ill in the opposite direction, this having the effect of decreasing the portion of said control resistance in parallel with relay coil 2|I5 and increasing the portion of said resistance in parallel with the relay coil 2 M. This will cause the relay coil 2 M to be energized more highly than relay coil 2l5, this causing the switch arm 2H to be brought into engagement with contact 2 l2. Engagement of switch arm 2! i with contact 2l2 will cause energization of the motor field coil E59 by a circuit as follows transformer secondary 2%, wire 225, wire 2MB, field coil I122, wire 263,-contact 2l2, switch arm 2H, wire 262, wire 228 and wire 229 to transformer secondary 222. This will cause rotation of the motor shaft 952 in a direction to close the damper it and to rotate the balancing arm Hit in a This rotation of is in parallel with the relay coil 2M and increasing the portion of such resistance which is in parallel with the relay coil 2 l 5. This will have the efiect of decreasing the current fiow in relay coil 2M and increasing the current flow in relay coil 2E5. When the movement of the balancing arm I162 is sufficient to overcome the initial unbalancing action of the controller 9| the relay coils will again be balanced thereby causing switch arm 2| i to disengage from contact 2l2, this causing stopping of the proportioning motor 90 in its new position. It should now be apparent that the position assumed by the proportioning motor will vary in acordance with the position of the control arm ill] on the control resistance I1 I further be apparent that as the temperature of the return air falls the damper l3 will progressively be moved towards open position, and that as the return air temperature rises the damper l3 will be progressively moved towards closed position. 1

If the relative humidity within the conditioned space should increase the control arm I82 of the humidity controller 92 will be moved in a clockwise direction across the control resistance H83, this acting to reduce the portion of control resistance I83 which is in parallel with the relay coil 2% and to increase the portion of said resistance which is in parallel with relay coil 2M.

' This will have the eif-ect of reducing the current flow in relay coil 2I5 and increasing the current flow in relay coil 2M, this action causing the switch arm 2H to be brought into engagement with the contact 2|I2, this causing rotation of the proportioning motor in a direction to move the by-pass damper towards closed position. Under this action the balancing arm lot will be rotated in a counter-clockwise direction across the balancing resistance Nil, vthis having the effect of reducing the current flow in relay coil 2 it and increasing the current flow in relay coil M5 to thereby reduce the initial unbalancing effect caused by the controller 92. When the movement of the proportioning motor is sufficient to cause the balancing potentiometer to balance out the initial unbalancing action of the controller 92, the relay 205 will cause stopping'of the motor at this point. In a similar manner, if the relative humidity within the space should decrease the humidity controller will act to unbalance the relay 205 in the opposite direction, this causing ro- It should tation of the motor shaft H2 in a direction to open the by-pass damper l3, and the amount of opening movement will be dependent upon the initial unbalancing action of the controller 92. The humidity controller 92 therefore acts to increase the opening of the by-pass damper it as the relative humidity within the conditioned space decreases and to decrease the opening of the bypass damper l3 as the relative humidity in- I creases.

Upon a decrease in outside temperature the control arm I98 of the controller 93 will move to the left across the control resistance I99, this having the eifect of decreasing the portion of control resistance I99 which is in parallel with the relay coil 2% and increasing the portion of said resistance which is in parallel with the relay coil 2 it. This will cause a greater current flow in relay coil 2M than occurs in relay coil 2%, this having the effect of moving the switch arm 2M into engagement with contact 2 l2 thus energizing field coil 859. This causes the motor shaft M2 to be rotated in a direction to close the damper it and to move the balancing arm ltt upwardly across the balancing resistance itl. This movement of the balancing arm ltd will decrease the portion of balancing resistance Mill in parallel with the relay coil 2M and increase the portion of said resistance which is in parallel with relay coil 2E5. The effect thus will be to compensate for the initial unbalancing effect of the controller 93. When the damper has been moved sufficient- 1y to cause the balancing potentiometer to fully compensate for the unbalancing effect of controller 93 the proportioning motor will stop in this new position. In a similar manner, as the outside temperature increases the control arm I98 of the controller 93 will move to the right across control resistance I99, this in a manner which should now be apparent, causing rotation of the proportioning motor in a direction to open the by-pass damper l3.

It will be noted'that the rheostat 246 is interposed between the balancing arm ltll and the junction of the relay coils 2 land 2 it. The purpose of this rheostat is to desensitize the balancing potentiometer to thereby make the operatingrange of the controller 90 less than its total range. In other words, by reducing the current flow through the balancing arm ltt this arm must travel a greater distance across the resistance ltfl to have the same effect upon the relative energizations of relay coils 2M and 2 it than would be necessary if the resistance of rheostat 2% were not present. Therefore, a relatively small movement of the control arm I'm across the control resistance Hi may effect such an unbalancing of the energizations of relay coils 2 it and 2% that it will require movement of the balancingarm lltt across the entire range of movement on resistance Hill to cause rebalancing. Thus by properly adjusting the rheostat 2% the proportioning motor may be made to move the by-pass damper it from a full open position to a full closed position upon movement of the control arm till across but a fraction of its range. For instance, while the controller 91 has a total range of 8 F., movement of the control arm l'ltl through an angle corresponding to but 2 F. will cause movement of the by-pass damper from one extreme position to the other. a

As hereinbefore pointed out, the humidity controller 92 aflects the positioning of by-pass damper 13 on a rise in humidity in the same manner as the temperature controller 98 acts upon a rise in temperature. In other words, upon a rise in temperature the controller 9| acts to close the by-pass damper I3 and upon a rise in humidity the humidity controller 92 acts to move the bypass damper I3 further towards closed position. Conversely, upon a fall in temperature the temperature controller 9| will act to move the bypass dampers further towards open position and if the humidity should fall the humidity controller 92 will cause additional movement of the by-pass damper I3 to open position. The effect of the humidity controller, therefore, is to vary the relationship between the temperature controller 9| and the proportioning motor 90 in a manner to compensate for changes in humidity. Thus, should the humidity within the space fall, it will have the same effect upon the proportioning motor as would occur if the temperature within the space should fall. In other words, even though the temperature controller I'IIl remains stationary, the proportioning motor will be caused to move the by-pass damper towards open position. In order for the temperature controller 9| to bring the damper back to its original position the control arm I'Il] must be moved across the control resistance I II in a counterclockwise direction, this requiring that the temperature of the return air increase. The action of the humidity controller 92, therefore, is to change the location of the operating range of the temperature controller 9| within its total range of operation. Or put another way, the humidity controller 92 acts to change the control point of the temperature controller 9| in accordance with changes in humidity. It will be noted that the rheostat 253 is interposed between the control arm of the humidity controller and the junction of the relay coils 2 I4 and H5. The purpose of this rheostat is to provide adjustment of the effect of the humidity controller on the controller 9|. By increasing the resistance in this circuit the effect of the controller 92 will be reduced while'by decreasing this resistance the effect of the controller 92 on the temperature controller 9| will be increased. In this manner the change in control point of the temperature controller for a given change in humidity may be determined. By properly adjusting this resistance the humidity controller may be made to change the temperature controllers control point in a manner to maintain a constant effective or comfort temperature.

The function of the outdoor temperature controller 93 is likewise to change the control point of the temperature controller 9|. In present air conditioning practice it is considered desirable to vary the temperature maintained within the conditioned space in accordance with outside temperature instead of maintaining the temperature within the space at a constant value, the purpose of this being to avoid shock to persons entering the space from outside and also to conserve on operating costs. As hereinbefore pointed out, the outdoor temperature controller 93 acts in opposition to the indoor temperature controller 9|. In other words, upon an increase in indoor temperature the controller 9| will act to move the by-pass damper I3 towards closed position. Upon an increase in outdoor temperature, however, the controller 93 will act to move the by-pass damper I3 towards open position. Therefore, if the indoor temperature should remain constant but the outdoor temperature increase, the temperature controller 93 will act to move the damper I3 to open position. In order for the temperature controller 9| to cause movement of the by-pass damper I3 back to its original position, the space temperature must be increased. In this manner, therefore, the outdoor temperature controller acts to raise the control point of the temperature controller 9| as outdoor temperature increases. Conversely, as the outdoor temperature decreases the outdoor temperature responsive controller 93 will act to lower the control point of the indoor controller 9|. It will be noted that the rheostat 25I is interposed between the control arm I98 of the outdoor controller and the junction of relay coils 2H3 and 2|5. The purpose of the rheostat 25I is to vary the effect of the outdoor controller upon the control point of the indoor controller 9|. If desired this rheostat may be so adjusted that a 1 F. change of indoor temperature has the same effect upon the proportioning motor as would occur for a.3 F. change in outside temperature. Therefore, with such adjustment for each 3 F. rise of outside temperature the control point of the controller! will be raised 1 F. Therefore, when the outdoor temperature is below the range of the controller 93 the indoor controller will be adjusted to maintain a return air temperature of 72 As the outdoor temperature rises above 76 F. the control point of controller 9| will be raised 1 for every 3 of such outdoor temperature rise and thus when the outdoor temperature becomes 100 F, the controller 9| will act to maintain a return air duct temperature of 80".

From the foregoing it should be apparent that the by-pass damper I3 is controlled to maintain primarily a constant return air temperature which is determined by outdoor temperature and inside relative humidity. When the return air temperature increases the by-pass damper will be. moved towards closed position, this causing an increase in flow of air through the refrigerated spray water issuing. from the spray pipe 3 and decreasing the portion of the air by-passed around such spray. This will have the effect of increasing the amount of cooling. Therefore, as the return air temperature increases the return air temperature controller 9| will act to increase the cooling effect of the air correspondingly. Also it should be apparent that the return air temperature controller 9| is adjusted by the humidity controller to maintain a constant effective temperature. In other words, as the humidity within the space increases the return air temperature controller will be adjusted to maintain a lower temperature, thereby compensating for the effect upon human comfort of such rise in humidity. Furthermore, it should be apparent that the return air temperature maintained will be varied in accordance with a predetermined schedule with variations in outdoor temperature.

It will be remembered that the operation of the system just described occurs only when the steam valve 95 is closed. If now, should the return air temperature fall sufficiently to cause opening of the steam valve, the resulting rotation of cam ZII will cause switch arm 213 to disengage contact arm ZMa, and to engage contact arm 214. This will disconnect the control arms I10, I82 and I98 from the connected ends of the relay coils, and also cause short-circuiting of relay coil 2I5 by a circuit as follows: upper end of relay coil 2| 5, wire 221, wire 221a, switch arm 213, contact arm 214, wire 215', and wire 231 to lower end of relay coil 2I5. This short-circuit of relay coil 2|5 completely unbalances the relay, causing switch arm 2 to engage the contact 2I2, this causing energization of field coil I59 and rotation of the shaft I52 in a direction to completely close the by-pass damper I3. Due to the complete short-circuiting of the relay coil 2 I 5 the balancing potentiometer will be incapable of rebalancing the relay and consequently the damper I3 will be completely closed. It should therefore be apparent that when the steam valve 95 is opened, the by-pass damper I3 will be moved to complete closed position regardless of the return air temperature. When, however, the steam valve 95 is completely closed the control of the by-pass damper I3 will be effected in the manner hereinbefore described.

The purpose of the corrector resistance I13 and the corrector arm I12 is to effect proper operation of the controller 9I when the control arm I1 approaches either of its extreme positions. For a more detailed description of the function of the corrector resistance I13 and of the compensated control system just described, reference is made to my co-pending application, Serial No. 38,446, filed September 3, 1935. While for the sake of clearness I have omitted the usual limit switches, it will be understood that such limit switches may be employed. For a disclosure of such limit switches reference is made to Patent No. 1,989,972 issued to Lewis L. Cunningham on May 22, 1935.

The proportioning motor 99 comprises a pair of rotors 289 and 28I mounted upon a shaft 283.

Interposed between the shaft 283 and the proportioning motor shaft 219 is a gear train 294. R- tation of the shaft 293 under the action of rotor 299 or 29I therefore causes rotation. of the shaft 219. Cooperating with the rotors 289 and 28I are field coils 285 and 286 respectively. The rotor 289 and field coil 285 comprise amotor for driving the shaft 219 in one direction while the rotor 28! and field coil 289 comprise a motor for driving the shaft 219 in the opposite direction. Also mounted upon the shaft 219 of the proportioning motor is a balancing arm 299 which is arranged to. cooperate with a balancing resistance 29i to form a balancing potentiometer. When the valve 95 is completely closed the balancing arm 299 engages the extreme lower end of the balancing resistance 29I as shown. As the valve is opened, however, the arm 299 is moved upwardly across balancing resistance29l and when the valve is completely opened arm 299 engages the extreme upper end of resistance 29I.

Reference character 295 designates generally a balanced relay identical with the balanced relay 2.95 previously described. This relay comprises a U-shaped armature pivoted at 296 and having legs 291 and 298. Cooperating with the leg 291 is a relay coil 299 while a similar relay coil 399 cooperates with the leg 299. Secured to the armature by an insulating member 39I is a switch arm 392 which isadapted to cooperate with the contacts 393 and 394. When the relay coils 299 and 39 are equally energized the armature assumes the position shown, in which switch arm 392 is midway between the contacts 393 and 394. If, however, coil 299 is energized more highly than coil 39, switch arm' 392 will engage contact 393 and if the coil 399 is energized more highly than coil 299, switch arm 392 will engage the contact 394.

Reference character 395 designates a step-down transformer, the primary of which is connected to the line wires 222 and 223. One side of the secondary 39B is connected by a wire 391 to the lower end of relay coil 299. A wire 398 connects the upper ends of the relay coils 299 and 399 while the lower end of relay coil 399 is connected by wires 399 and 3I9 to the other terminal of the transformer secondary 396. In this manner the relay coils 299 and 399 are connected in series across the terminals of the transformer secondary. A wire 3I I is connected at one end to the junction of wires 399 and 3 I0 and at its other end to a resistance 3I2, the other end of this resistance being connected by wires 3I3, 3I4 and M5 to one end of the balancing resistance 29I and to one end of the control resistance I99 of the return'duct temperature controller I99. The other ends of the balancing resistance 2! and the control'resistance I98 are connected by wires 3I6, 3| 1, 3I8 and 3I9 to resistance 329. Resistance 329 in turn is connected by wires 32I and 322 to the transformer secondary and to the lower end of relay coil 299. In this manner the control resistance I98 and the balancing resistance 29I are connected in parallel across the terminals of the transformer secondary 396 along with the 'relay coils 299 and 399 which are serially connected across said transformer secondary. Connected to the junction 398 for the relay coils 299 and 399 is a wire 323 which joins the wire 324 leading to the balancing arm 299 of the balancing potentiometer. Wire 323 is also connected to a wire 325 leading to the mercury switch I24. A wire 329 leads from the wire 325 to the control arm II8 of the low limit controller I9I. 321 leads from the right end of the mercury switch I24 to the left end of the control resistance 'I I9 of the low limit controller I9I, and a wire 329 leads from the junction of the wire 321 and resistance l I9 to the control arm I91 of the return duct controller I99. A wire 339 leads from the right-hand end of the control resistance II9 of the low limit controller to the left-hand end of the mercury switch I24, and a wire 33!! leads, from the same end of the mercury switch I24 to the junction of wires 3I8 and 3I9.

With the parts in the position shown, the apparatus is operating under a summer cycle. For convenience in description it will be assumed that the system is now operating on the heating cycle instead of the cooling cycle as illustrated in the drawings. Under this condition the mercury switch I29 will be tilted in the opposite direction due to the fact that the return air temperature is below 13 (the setting of controller I92). Also under the heating cycle the discharge duct temperature will be assumed to be higher than 63. The control arm IIB of the low limit controller l99 will therefore engage the extreme left-hand end of control resistance H9 at this time. With this position of the control arm M8 the control arm I91 of the return duct controller I99 willbe connected to the junction of the relay coils 299 and 39 by wires 398, 323, 325, 326, control arm H9 and wire 329. Also due to the wires 339 and 33E. being connected through mercury switch I39, the right-hand end of control resistance II9 will be connected to the lower end of relay coil 299 by means of wires 339, mercury switch I29, wires 33I and 3I9, resistance 329 and wires 32I, 322 and 391. As the control arm H8 is now engaging the extreme left-hand end of control resistance II9, the left-hand end of said resistance is connected by the control arm M8 to the junction of coils 299 and 399. Due to the right-hand end of said resistance being connected to the lower end of relay coil299 as just described the resistance A wire I I9 will be connected entirely in parallel with the relay coil 299. To compensate for the unbalancing effect on the relay caused by the control resistance H9 being in parallel with the relay coil 299, a resistance 332 is shown as connected between wires 3I3 and 323. This resistance, it will be observed, is in parallel with the relay coil 300. Since this resistance is of equal value to that of resistance H9 there will be no unbalancing effect of the relay 295 due to the control arm I I 8 of the low limit controller IOI engaging the extreme left-hand end of the control resistance I I9.

Assuming now that the return air duct temperature is 70, the control arm I01 will be engaging the center of control resistance I08. Assuming also that for this condition the valve is half open and the balancing arm 299 is engaging the center of balancing resistance 29I, the relay 295 will be balanced and the proportioning motor will be deenergized in this position. If now the return air temperature should increase, the control arm I01 will move towards the left across V current flow in relay coil 299.

control resistance I08, this decreasing the portion of said control resistance in parallel with the relay coil 300 and increasing the portion of said resistance in parallel with relay coil 299. This will cause a greater current flow in relay coil 299 than occurs in the relay coil 390, this causing switch arm 302 to engage contact 303 thereby energizing the motor field 285 by a circuit as follows: transformer secondary 306, wire 322, wire 333, switch arm 302, contact 303, wire 334, motor field 285, wire 336 and wires 3H and 3| 0 to transformer secondary 306. This will cause rotation of the motor shaft in a direction to close the steam valve 95, this moving the balancing arm 290 downwardly across the balancing resistance 29I. This, in a manner which should now be apparent, acting to reduce the current flow in relay coil 299 and increase the current flow in co-il 300. When the movement of the balancing arm is suflicient to neutralize the initial unbalancing action of control I 00, the proportioning motor will stop with the valve in its new position. Conversely, upon fall in return air temperature the control arm I0I-of the return duct controller will move in the opposite direction across control resistance I08, this having the effect of decreasing the current flow in relay coil 299 and increasing the current flow in relay coil 300, this causing switch arm 302 to engage contact 304 thereby energizing the motor field 286 as follows: transformer secondary 306, wire 322, wire 333, switch arm 302, contact 304, wire 337, motor field 286, and wires 336, 3H and M0 back to secondary 306. This action will cause movement of the valve towards open position and movement of the balancing arm 290 upwardly across balancing resistance 29I, this having the effect of decreasing t e current flow in the relay coil 300 and increasing the When the movement of the balancing arm 290 is sufficient to neutralize the initial unbalancing action of controller I00 the relay 295 will again become balanced-and the switch arm 302 will disengage contact 304 causing the proportioning motor to stop with the valve in this new position. In this manner the controller I00 will act to position the steam valve in accordance with the temperature of the return air, this controller acting to cause anincrease in steam flow to the reheating coil as the temperature decreases and to decrease the flow of steam as the return air temperature increases, and in this manner acts during the heating cycle to maintain the temperature of the return air between 69 and 71.

With the return air temperature above 63 F. it will be rerembered the control arm II8 of low limit controller I 0! engages the extreme lefthand end of the control resistance II9. With this position, as previously pointed out, the entire control resistance H9 is connected in parallel with the relay coil 299. If now should the delivery duct temperature fall below 63 F. the control arm I I8 will be moved to the right across the control resistance H9. This will have the effect of placing part of the control resistance H9 in parallel with the relay coil 300 and consequently decreasing the portion of control resistance II9 which is in parallel with the relay coil 299. The effect of this will be to decrease the current'fiow in relay coil 299 and to increase the current flow in relay coil 300, this causing engagement of switch arm 302 with contact 304 to cause rotation of the proportioning motor shaft in a direction to open the valve. The balancing arm 290 during this valve opening movement will be moved upwardly across the balancing resistance 29I, this decreasing the current flow in relay coil 300, and increasing the current flow in relay coil 299. When the movement of the balancing arm is sulficient to neutralize the unbalancing effect of low limit controller I I9, the relay will become balanced, this causing stopping of the motor with the valve in this further opened position. It will be apparent that upon further fall in the delivery air temperature the control arm I I8 of the low limit controller will move further across the control resistance this causing the steam valve 95 to be opened to a wider position. Thus when the temperature of the delivered air falls to 60 F. the valve will be caused to assume a complete wide open position irrespective of the temperature of the return air. The low limit controller I M therefore acts to place the return air temperature controller I00 in full control of the steam valve whenever the delivered air temperature is above 63 F. As the delivered air temperature falls below this value, however, the low limit controller will progressively cause opening of the steam valve to offset or stop this falling in temperature. In this manner the low limit controller prevents delivery of air to the spaces 9 and I0 below 63 F. during the heating cycle, thereby avoiding chilling of the occupants by cold drafts.

During the cooling cycle it is necessary to deliver air to the spaces 9 and I0 below 63 F. in order to provide adequate cooling of the spaces during hot weather. It is therefore necessary on the cooling cycle to disconnect the low limit controller IOI so as to prevent turning on of the steam valve 95 by such controller. This is the function of the controller I02. As previously pointed out, this controller is set so as to assume the position shown when the return air temperature is above 73 F. and to assume the opposite position at lower temperatures. As under the heating cycle the return air temperature is below 73 F. and as during the cooling cycle the return air temperature is above this value, the controller I02 will automatically shift its position as the operation of the system changes from heating to cooling. Therefore, during the cooling cycle the controller I02 will assume the position shown. With the mercury switch I24 tilted as illustrated in the drawing the right-hand end of the control resistance I I9 of the low limit controller will be disconnected from the relay 295. Also the control arm I01 of the return air temperature controller I will be directly connected to the junction wire 308 of the relay coils 299 and 300 by wires 323, 325, mercury switch I24, wire 321 and wire 329. Under this condition the return air temperature controller. I00 will be placed in full control of the steam valve and the low limit controller will have no effect whatsoever due to the fact that the control resistance H9 is short-circuited through the mercury switch I24 and also due to the fact that the right-hand end of the control resistance I I9 is disconnected from the relay 295 by the mercury switch I24. The delivery duct temperature may therefore fall below 60 F. without the low limit controller acting to cause opening of the steam valve. As under the cooling cycle the return air temperature will be above 71 F. the controller I00 will act to cause the valve to move to full closed position as illus-,

trated in the drawing.

Operation With the parts in the position shown, the outdoor temperature is approximately 88 F. as indicated by the control arm of the outdoor temperature controller assuming an intermediate position. Also the return air temperature is approximately 76 F. as indicated by the control arm I'IIl of the temperature controller 9I being in an intermediate position. The relative humidity within the spaces is approximately 50%, this causing the controller 92 to assume an intermediate position. Due to the intermediate positions of all of these controllers the proportioning motor 90 has moved the by-pass damper to a position midway between open and closed positions. Also the temperature of the air issuing from the spray is approximately 53 F. as indicated by the dew-point controller 35 assuming an intermediate position. This causes the three-way valve 22 to assume a position in which a mixture of cold water from the receiver 20 and return water from the trough 26 is supplied to the spray 3. With the parts in the position shown; therefore, the system is operating on the cooling cycle to maintain a'temperature in the spaces 9 and In which is below-outside temperature. As the system is operating on the cooling cycle the temperature of the delivered air is below 60 F. this causing the low limit controller IOI to assume an extreme position. However, as the return air temperature is above '73 F. the controller I02 has placed the low limit controller .IIII out of operation, this permitting the temperature controller I00 to completely close the steam valve 95. Therefore, no steam is being supplied to the reheater 40. Also at this time .the booster heater controlvalves I32 and I33 are completely closed by their respective temperature controllers I40 and HI due to the temperature of the air within the spaces 9 and I0 being above the range of such temperature controllers. At this time also the steam valve I5 for the preheater 2 is completely closed due to the temperature of the air issuing from the spray being above the range of the controller 80. No heat whatsoever, therefore, is being supplied to the spaces 9 and I0 by the system and the system is operating under the control of the return air temperature controller 9| and the humidos'tat 92, these controllers acting to adjust the by-pass damper I3 in a manner to maintain a constant effective comfort temperature'within the spaces 9 and I0, the value of this effective temperature being determined by the outside temperatur controller 93.

If now should the outside temperature increase, the outside temperature controller, in a manner hereinbefore described, will cause the by-pass damper I3 to be moved towards open position, this having the effect of increasing the portion of the air by-passed around the cooling spray 3 and raising the control point of the controller 9|. As the cooling load will increase due to this increase in outside temperature and as the cooling effect of the system has been decreased by the outside temperature controller, the return air temperature will begin to rise. This rising temperature will cause the controller 9| to gradually close the by-pass damper I3, this increasing the cooling effect of the system thereby acting to counteract the temperature rise. When the temperature rise has reached the new control point of the controller M as determined by the outside temperature controller 93, the closing movement of the damper I3 by the controller 9| will be sufficient to cause the cooling effect of the system to be equal to the cooling load, thereby preventing further increase in temperature within the spaces 9 and I0.

While the return air temperature controller Si is moving the by-pass damper I3 towards closed position, as described in the preceding paragraph, the portion of the return air passed through the spray 3 will be increased, this increase in air flow causing the temperature of the air issuing from said spray to increase. This will cause the dew-point controller 35 to gradually cause movement of the three-way valve 22 in a direction to decrease the portion of re-circuiated water and to increase the portion of the Water withdrawn from the receiver 20 which is delivered to the spray. It will be seen, therefore, that as the cooling load upon the system increases due to increase in outside temperature the quantity of refrigerated water passed to the spray 3 will be increased, thereby increasing the cooling action of said spray. Due to the relatively wide range of the dew-point controller 35 this increase in the supply of refrigerated water passed to the spray. 3 will not be sufiicient to fully counteract the temperature rise of the air issuing from the spray. For instance, it will be seen that with the controller 35 in the position shown, a dew-point temperature of 53 F. is being maintained. In order to cause the portion of refrigerated water supplied to the spray to be increased the temperature at the bulb 45 must increase and before all refrigerated water is supplied to the spray 3 the temperature of the air issuing from the spray must have risen from the 53 F. to 56 F. It should therefore be apparent that as the refrigerating load increases the dew-point temperature of the air issuing from the spray will be allowed to increase by the controller 36. This will result in a higher humidity occurring within the spaces 9 and I0 at this time. This action is desirable for as the outside temperature increases it is desired, as hereinbefore pointed out, to raise the effective temperature maintained within the spaces 9 and I9 to avoid shock to persons entering the spaces from outside. Due to this decrease in dehumidifying action caused by raising the dew-point of the air issuing from the spray, the humidity within the spaces will be raised as well as the temperature to effect this desired rise in effective temperature.

Should the outside temperature now fall the outside temperature. controller 93 will in effect lower the control point of the controller 9I, this causing the by-pass damper I3 to be moved further to open position. As upon falling outside temperature the cooling load will decrease and as the cooling effect of the system has been increased due to the lowering of the control point of controller 93, the return air temperature will begin to fall. As this return air temperature falls the controller 9| will act to gradually increase the opening of the by-pass damper I3 thereby decreasing the portion of the return air passed through the cooling spray and increasing the portion of such air by-passed around this spray. When the return air temperature falls to the new control point of the controller 9I the opening of the by-pass damper I3 will be sufficient to reduce the cooling effect of the system enough to prevent further fall in temperature. The temperature controller 9| and the humidity controller 92 will then act to maintain this new standard of effective temperature within the spaces 9 and III.

While the y-Dass damper I3 is moved towards open position, as described in the preceding paragraph, the air fiow through the spray 3 will decrease, this causing the temperature of the air issuing from the spray to decrease which results in causing the dew-point controller 35 to adjust the three-way valve 22 to decrease the portion of cold water supplied from the receiver 2I to the spray 3. Due to the wide range of the controller 35 this decrease in refrigerated water supplied to the spray will not fully compensate for the decrease in temperature of the air issuing from the spray. Therefore, as the outdoor temperature decreases the cooling load upon the system will decrease, this eventually resulting in the controller 9| increasing the opening of the bypass damper I3, this resulting in a reduction in the air flow through the spray 3, this reduction in air flow causing the temperature of the air issuing from the spray to fall due to the fact that the wide range dew-point controller 35 will not reduce the flow of refrigerated water sufliciently to compensate for the decrease in air flow through the spray. This decrease will cause a reduction in humidity within the spaces at this time, thereby causing the desired reduction in effective temperature to be comprised of a reduction in humidity as well as a reduction in temperature.

As the outdoor temperature continues to fall the cooling effect of the system in the manner described will continue to be decreased and when the outside temperature falls to, say, 76 F. the control point of the indoor controller 9| will be shifted to maintain an indoor temperature of 72. At this time the by-pass damper l3 will be almost completely open. this causing but a small portion of the air to be passed through the spray 3. Very little cooling effect will thus be required and consequently the controller 35 will cause the three-way valve 22 to assume a position in which substantially all of the water supplied to the spray is re-circulated water. At this time also the dew-point temperature maintained by the controller 35 will be at a minimum, for instance 50 F. As the outside temperature continues to fall the. inside temperature will fall due to the decrease in cooling load and as it approaches 70 F. the by-pass damper I3 will be moved to wide open position so that a minimum amount of air is passed through the spray 3. At this time the controller 35 will stop entirely the flow of refrigerated water to the spray 3, this resulting in the temperature of the water within the receiver 20 falling below the setting of the controller 65, this placing the refrigerating system out of operation. It should therefore be apparent that when the outside temperature falls sufiiciently to result in the inside temperature falling below 72 F. the cooling system will be placed completely out of operation.

At this time the controller I02 will have placed the low limit controller IllI in operation thereby preventing delivery of air to the spaces 9 and I0 below 60 F. As the outside temperature continues to fall the temperature within the spaces 9 and I0 will fall, this resulting in the return air temperature dropping. When the return air temperature begins dropping below 71 F. the return air temperature controller I00 will begin gradually opening the steam valve 95 to supply heat to the spaces 9 and I0. As hereinbefore pointed out, when the steam valve 95 begins to open the auxiliary switch 212 will be actuated, this causing the by-pass damper I3 to be completely closed thereby causing all of the return air to be passed through the spray. Upon further decrease in outside temperature the heat loss from the spaces 9 and ID will increase, this having the tendency of reducing the temperature of the air returning from said spaces, this reduction in temperature acting upon the temperature controller I09 to increase the supply of steam to the heater 4 thereby increasing the amount of heat supplied to the spaces. It will therefore be seen that as the'heating load increases the supply of steam to the reheater 4 will be increased correspondingly. Due to the controller I00 being responsive to the return air temperature which is a mixture of the air drawn from both spaces, the supply of steam to the reheater will be controlled in accordance with the average temperature of the spaces 9 and I0- At this time the controllers I40 and I in the spaces 9 and II] will act to supply proper amounts of steam to the booster heaters I30 and I3I in order to maintain proper temperatures within each zone. By the use of these individually controlled booster heaters the temperature in each zone is maintained constant even though the heating load of said spaces may vary relatively to each other.

It will be remembered that during the heating cycle the by-pass damper I3 is completely closed due to the steam valve 95 being open. The spray at thistime will therefore act to humidify the air being passed through to the spaces 9 and I0. In order to maintain proper relative humidity within the spaces 9 and I 0 the temperature of the air issuing from the spray is maintained in the neighborhood of 40 F. Due to the air issuing from the spray being in a saturated condition this 40 F. will thus be the dew-point temperature of the air. When this air is discharged into the spaces 9 and II) in which the temperature is maintained at approximately 70 F., this relative humidity will be approximately 35%, which is desirable. This dew-point temperature of approximately 40 F. is maintained by the dewpoint temperature controller 80 which controls the supply of steam to the reheater 2. Thus as the dew-point temperature falls the steam supply valve 18 is opened to supply more steam to the reheater therebymaintaining the dew-point temperature at its proper value.

From the foregoing it should be apparent that I have provided an air conditioning system for year-around operation, this system acting in summer to maintain an effective temperature within the spaces 9 and II] which is varied in accordance with changes in outside temperature. It should further be apparent that the system is entirely automatic, changing from summer cooling operation to winter heating operation without any manual adjustments whatsoever. While for purposes of description I have assumed specific values of temperature and other conditions for the various controllers, it will be apparent that these values may be varied as desired for each individual installation. It will also be apparent that while I have shown the system as conditioning but two separate zones, the system may be employed for conditioning as many zones as desired, and if desired, may be used for conditioning but a single zone. Many other changes which are within the scope of my invention will suggest themselves to those skilled in the art and I therefore desire to be limited only by the scope of the appended claims and the prior art.

I claim as my invention:

1. In an air conditioning system, in combination, a conditioning chamber having an inlet and an outlet, duct means connecting said outlet with a space to be conditioned, condition changing means for changing the heat content of the air passing through said chamber, by-pass means for by-passing a portion of the air around said condition changing means and mixing it with the conditioned portion, damper means for controlling the relative proportions of the by-passed air and the conditioned air, motor means for positioning said damper means, air condition responsive means in control of said motor means, a second condition changing means for changing the heat content of the air, means for placing said second condition changing means into and out of operation, and automatic means for closing said by-pass when said second condition changing means is placed into operation.

2. In an air conditioning system, in combination, a conditioning chamber, means connecting said chamber with a space to be conditioned, a first conditioning means in said chamber for changing the heat content of the air, a second conditioning means in said chamber for changing the heat content of the air, a by-pass around said first conditioning means, damper means for controlling the relative proportions of the air passed through said first conditioning means and said by-pass, condition responsive means for controlling said first and second conditioning means and said damper means, and means for moving said damper means to an extreme position when said second-conditioning means is actuated from an extreme condition of operation.

3. In an air conditioning system, in combination, a conditioning chamber having an inlet and an outlet, duct means connecting said outlet with a space to be conditioned, means for reducing the heat content of the air passing through said chamber, by-pass means for by-passing a portion of the air around said heat content reducing means and mixing it with the conditioned portion, damper means for con-trolllng the relative proportions of the by-passed air and the conditioned air, motor means for positioning said damper means, means responsive to the temperature of the air in said space for controlling said motor means, means for heating the air, thermostatic means responsive .to said space [temperature for controlling said heating means, and means actuated by said thermostatic means additionally controlling said motor means.

4. In an air conditioning system, in combination, a conditioning chamber having an inlet and an outlet, duct means connecting said outlet with a space to be conditioned, means for reducing the heat content of the air passing through said chamber, by-pass means for by-passing a portion of the air around said heat content reducin means and mixing it with the conditioned portion, damper means for controlling the relative proportions of the by-passed air and the conditioned air, motor means for positioning said damper means, means responsive to [the temperature of the air in said space for controlling said motor means to increase the proportion of the air by-passed as the space temperature falls, means for heating the air, means for placing said heating means into operation when the space temperature falls to a predetermined value, and automatic means for closing said by-pass when said heating means is placed into operation.

5.In an air conditioning system, in combination, a conditioning chamber having an inlet and an outlet, duct means connecting said outlet with a space to be conditioned, condition changing means for changing the heat content of the air passing through said conditioner, by-pass means for by-passing a portion of the air around said condition changing means and mixing it with the portion passed through said condition changing means, damper means for controlling the flow of air through said by-passmeans and said condition changing means, motor means for positioning said damper means, temperature varying means for varying the temperature of said air mixture, means responsive to space temperature for controlling said motor means and said second temperature varying means, and means for moving said damper means to an extreme position when said temperature varying means is placed into operation.

'6. In an air conditioning system, in combination, a conditioning chamber having an inlet and an outlet, duct means connecting said outlet with a space to be conditioned, means for spraying water into the air passing through said conditioner, by-pass means for by-passing a portion of the air around said spray means and mixing it with the sprayed portion, damper means for controlling the relative proportion of the by-passed air and the sprayed air, motor means for positioning said damper means, condition changing means downstream of said spray and by-pass means for changing the heat content of the air mixture, air condition responsive means in control of said damper motor means and said condition changing means, and means for causing said damper motor means to move to an extreme position when said condition changing means is placed into operation.

7. In an air conditioning system, in combination, a conditioning chamber having an inlet and an outlet, duct means connecting said outlet with a space to be conditioned, means for spraying wa-. ter into the air passing through said conditioner, by-pass means for by-passing a portion of the air around said spray means and mixing it with the sprayed portion, damper means for controlling the relative proportion of the lay-passed air and the sprayed air, damper motor means for positioning said damper means, heating means downstream of said spray and'by-pass, means to thereby increase the temperature of the air mixture, temperature responsive means in control of said damper motor means and said temperature changing means, said temperature responsive means acting to progressively cause opening of said bypass as the space temperature falls and to place said heating means into operation when the space temperature falls to a still lower value, and means for closing said by-pass when said heating means is placed into operation.

8. In an air conditioning system, in combination, a conditioning chamber having an inlet and an outlet, supply duct means connecting said outlet to a space to be conditioned, dew-point control means in said conditioning chamber for maintaining a constant dew-point temperature of the air passing therethrough, by-pass means around said means last mentioned, temperature changing means for the air discharged from said dew-point temperature control means and said by-pass means, and temperature responsive means for controlling said temperature changing means and said by-pass means in a manner to close the bypass means and place said temperature changing means in operation.

9. In a system of the class described, in combination, a first controller, a second controller,

condition responsive means for operating said controllers, said means acting to progressively move one of said controllers from one extreme position to the other as said condition varies, and to begin moving the other controller from an extreme position as said condition varies further in the same direction, and means for moving said first controller to its opposite extreme position when said second controller is moved from the extreme position above mentioned.

10. In a system of the class described, in combination, a first controller, a second controller, condition responsive means for operating said controllers, said means acting to operate one of said controllers for one range of values of said condition, and to operate the other of said controllers for a different range of such values, and means for moving one of said controllers to an opposite position when the other controller is actuated by said condition responsive means.

11. In an air conditioning system, in combination, a conditioning chamber having an inlet and outlet, duct means connecting said chamber with a space to be conditioned, means for spraying water into the air passing through said chamber, cooling means for chilling said spray water, mixing valve means for controlling the temperature of said spray water, air heating means in said conditioning chamber on the upstream side of said spraying means for heating the air before it passes through said spray means, thermostatic means responsive to the temperature of the air on the downstream side of said spray means for controlling the temperature of said spray water, said thermostatic rneans including motor means for positioning said mixing valves in a manner to reduce the cooling effect of said cooling means on said spray water progressively as said temperature decreases, switching means actuated by said motor means to shut down said cooling means when the air temperature falls to a predetermined value, a second thermostatic means responsive to the temperature of the air on the downstream side of said spray means, said second thermostatic means acting to place said heating means into operation when the temperature of said sprayed air falls to a value lower than the value at which said first thermostatic means acts to shut down said cooling means, said second thermostatic means acting also to progressively increase the supply of heating fluid to said heating means as said air temperature continues to fall.

12. In an air conditioning system, in combination, a conditioning chamber having an inlet and outlet, discharge duct means connecting said outlet with a space to be conditioned, heating and cooling devices in said conditioning chamber, temperature responsive means controlling said heating and cooling means, thermostatic limit control means responsive to the temperature of the conditioned air for preventing said temperature from falling below a predetermined value, and thermostatic means for rendering said limit control means ineffective when said space temperature is above a predetermined value.

13. In an air conditioning system, in combination, a discharge duct for conveying air to a space to be conditioned, heating means for heating the air flowing through said discharge duct, cooling means for cooling the air flowing through saiddischarge duct, a thermostat responsive to the temperature in said space for controlling the heating means in a manner tending to maintain the space temperature constant, thermostatic limit control means responsive to the temperature of the air in said discharge duct for placing said heating means into operation independently of said space thermostat for preventing the temperature of the air'in the discharge duct from falling below a predetermined value, means for placing said cooling means into operation upon demand for cooling, and means also actuated upon demand for cooling for preventing said limit control means from maintaining the air temperature in said discharge duct above said predetermined value.

14. In an air conditioning system, in combination, a discharge duct for conveying air to a space to be conditioned, heating means for heating the air flowing through said discharge duct, a reversible electric motor for controlling said heating means, said motor having a control circuit, a first thermostatic switch, electric current controlling means responsive to space temperature and connected into said control circuit for causing said motor to assume various intermediate positions in a manner to maintain the temperature in the space substantially constant, a second thermostatic electric current controlling means responsive to the temperature of the air discharged to said space and connected into said control circuit in a manner to prevent the temperature of the discharge air from falling below a predetermined value irrespective of said 'first current controlling means, cooling means for cooling the air in said discharge duct, thermostatic means for placing said cooling means into operation upon demand for cooling, switching means connected into said control .circuit, said switching means having a first position wherein said second current controlling means is rendered efiective'to prevent the temperature of the discharge air from falling below a predetermined value and having a second position wherein said second current controlling means is rendered ineffective to prevent fall in temperature below said predetermined value, and means for .causing said switching means to be at its second position when the cooling means is in operation.

JOHN E. HAINES. 

